Picker stick check mechanism

ABSTRACT

A mechanism for controlling operation and positioning of a picker stick for a loom wherein a cam is interconnected with a picker stick member to simultaneously rotate with reciprocal pivotal movement of the picker stick. A pair of spring loaded cam followers engage the bearing surface of the cam and act as braking and positioning means controlling the picker stick during its reciprocal pivotal operating stroke. The particular shape of the cam determines the nature of the braking and positioning action which is effected by the cam followers during the operating stroke of the picker stick.

o United States Patent 11 1 1111 3,815,644 Skeen June 11, 1974 [54] PICKER STICK CHECK MECHANISM 3,119,417 1 /1964 Donoghue et a1. 139/149 x Inventor:' y Robert Skeen, Warwick, Ril- 3,228,430 1/1966 Paquette...., 139/162 [73] Assignee: Anthony Pace and Virgina Pace, Primary Examiner.lames Kee Chi d/b/a Magnatrol C0,, New York, Attorney, Agent, or FirmAlfred Musumeci NY.

22 Filed: Nov. 13, 1972 K h f F d mec amsm or contro mg operauon an position- [211 Appl' 305984 ing of a picker stick for a loom wherein a cam is interconnected with a picker stick member to simulta- 52 us. (:1. 139/162, 139/149 neously rotate with reciprocal pivotal movement of [51] Int. Cl D03d 49/40 the Picker StiCk- A pair of spring loaded cam followers [58] Field of Search 139/ l 6 1-165, engage the bearing Surface of the cam and act as brak- 139 4 ing and positioning means controlling the picker stick during its reciprocal pivotal operating stroke. The par- 5 References Cited ticular shape of the cam determines the nature of the UNITED STATES PATENTS braking and positioning action which is effected by the cam followers during the operating stroke of the 1,255,830 2/1918 Fmch 139/162 picker stick 2,120,199 6/1938 Burdett... 139/162 2,506,145 5/1950 French 139/162 X 16 Claims, 11 Drawing Figures PMENTEDJUH 1 1 I914 SHEET 10F 3.

FIG. I

PATENTEDJUW 19M 3315544 SHEET 20F 3 FIG.6

BACKGROUND OF THE INVENTION The present invention relates generally to mechanical apparatus especially useful in connection with textile machinery, and more particularly to a check mechanism 'for a loom picker stick.

Weaving of textile fabric or cloth is usually performed in a textile installation by a loom which operates to interweave the fibers forming the textile fabric in intermeshing relationship. In the operation of the loom, a first set of fibers is fed in a first direction and a second set of fibers is passed in a second direction transversely of said first direction to be interweaved with the fibers of said first set. Thus, as the first set of fibers moves in the first direction, the fibers of the second set are passed transversely to the direction of said first fibers and are weaved in an alternating manner about the fibers of the first set to form the fabric.

The transversely extending fibers of the second set are fed across the loom by a device known as a shuttle. The shuttle is-literally thrown back and forth across'the loom by a pair of picker sticks located on opposite sides of the loom. The path of the shuttle is directed by the lay beam of the loom, and as the shuttle moves back and forth from one side of the loom to the other it unwinds fiber forming the second set of transversely extending fibers-for the textile fabric being weaved.

Each of the picker sticks of the loom comprise vertically extending sticks which are mounted for pivotal motion at their bottom ends and which engage the shuttle at their upper ends to effect the back and forth movement of the shuttle in the operation of the loom. In its operating cycle, a picker stick will be pivotally actuated to impart an accelerating force to the shuttle to throw the shuttle across the loom to the opposite side thereof where it is then engaged by the other picker stick which performs a pivotal movement in a first direction after engagement with the shuttle to decelerate the shuttle by absorbing its momentum. After the picker stick has brought the shuttle to a complete stop during its decelerating pivotal motion, the picker stick is actuated to pivot in the opposite direction thereby to impart an accelerating force to the shuttle which it has engaged thereby throwing the shuttle across the loom to the picker stick on the opposite side which then engages the shuttle, decelerates it and brings it to a complete stop and then reverses its path by throwing it again across the loom to the other pickerstick.

Thus, each picker stick of a loom performs an operating cycle during the operation of the loom which involves pivotal reciprocal motion through a relatively small arc as it continuously decelerates and then accelerates the shuttle in the fabric weaving process. When the moving shuttle first abuts against the end of the picker stick, the momentum of the shuttle causes the picker stick to move through its pivotal arc in a first direction and as the picker stick moves through this pivoted arcuate path it gradually absorbs the momentum of the shuttle thereby decelerating the shuttle so that by the time the picker stick has reached one end of its path of motion the shuttle has been brought to a complete stop. At this point a strap mechanism actuates the picker stick in an opposite direction back through the arc of its travel and as this occurs the shuttle is accelerated in the opposite direction and when the picker stick reaches the opposite limit of its path of movement the shuttle becomes disengaged therefrom and is moving at a velocity sufficient to propel the shuttle to the picker stick on the opposite side of the loom.

'Eachof the picker sticks is equipped with a strap mechanism or similar device which imparts the accelerating movement to the picker stick, and with a check mechanism which operates to decelerate the picker stick and the shuttle when it is moved in the opposite direction. The present invention is primarily concerned with the check or braking mechanism whereby movement of the picker stick is controlled to decelerate the shuttle.

In the prior art, a variety of picker stick check mechanisms have been proposed but it has been found that problems persist with regard to smooth and effective decelerating operation of the picker stick. Proper control of the shuttle as it is moved back and forth across the loom is important in order to avoid imperfections in the fabric which is formed. If the shuttle is not properly controlled, imperfect fabric, generally referred to as seconds will be produced thereby greatly diminishing the economy of operation of the loom. Thus, in the operation of the picker stick smooth and effective control of the shuttle travel is necessary if there is to be avoided an unacceptably high percentage of imperfect material being manufactured by the loom. A'further consideration of major importance isthe cost and complexity of thepicker stick check mechanism. Most textile installations comprise a large number of looms each operating simultaneously. Since each loom will require a separate check mechanism for each picker stick, it will be apparent that the number of check mechanisms involved is quite high. Therefore, any savings which can be realized with regard to the cost of the check mechanism will be multiplied by the number of picker sticks involved and will usually amount to a rather signifi'cant sum. Accordingly, decreasingthe cost of manufacture of the check mechanism results in a significant advantage.

Simplicity of design and operation is an additional consideration of major importance. Diminishing the complexity of the overall design of the check mechanism will not only lower the cost thereof, but will also enhance the reliability of operation of such a mechanism. Since most looms are run continuously, any breakdown of a portion of the apparatus can involve significant loss in time and money if the loom must be taken out of production as a result. Thus, simplifying the design of the check mechanism in a manner which improves its dependability and extends it usable life will enable significant savings not only because machine breakdown is avoided but also because of the extended life of the equipment.

SUMMARY OF THE INVENTION Briefly, the present invention may be described as a mechanism for controlling operation of a-loom picker stick comprising a picker stick member mounted for reciprocal pivotal motion through an operating cycle, and a rotatably mounted cam which is interconnected with the picker stick member to be rotated jointly and which are mounted to engage the cam bearing surface on opposite sides of the cam. The cam follower members are biased by spring means which urge the followers against the cam bearing surface thereby providing a braking force against rotation of the cam. Since the cam is interconnected with the picker stick to be driven thereby during the picker stick operating stroke, the force applied by the cam followers acts as a braking and positioning force on the picker stick. As a result of the particular arrangement of the invention, the braking force which is applied to the picker stick and the positioning of the picker stick at various points in its operating stroke may be effectively controlled and determined by shaping the bearing surface of the cam in a particular manner to effect a desired control over the picker stick motion.

By a further aspect of the invention, the mechanism includes means whereby the relative angular position between the picker stick and the cam may be easily adjusted merely by manipulation of a series of set screws.

By a furtheraspect of the invention, there is included an internal lubricating system comprising a series of lubricating fluid passages whereby the various operating components and bearings of the picker stick check mechanism may be effectively maintained in a lubricated condition. I

DESCRIPTION oF THE DRAWINGS The present invention will be better understood by reference to the following detailed description thereof taken in connection with the accompanying drawings wherein:

FIG. I is a side elevation partially broken away of the picker stick check mechanism of the present invention;

FIG. 2 is a side elevation of the mechanism taken from the side opposite to that shown in FIG. 1;

FIGS. 30 3c are schematic diagrams showing the cam and followers of the present invention which illustrate three significant positions to which the cam is driven during the picker stick operating cycle;

FIGS. 4a 4c are side views partially in section of the mechanism whereby the relative angular positioning between the picker stick and the cam may be adjusted with one of three, different relative angular positions being illustrated in each figure;

FIG. 5 is a side elevation partially in section of a cover plate which enclosesa housing within which the cam and cam followers are mounted, with part of the internal lubrication system of the invention which extends through the cover plate being illustrated; and

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring now to thedrawings, particularly to FIGS. 1 and 2 thereof, the device of the present invention is shown as comprising a rigid frame structure upon which there is operatively mounted the picker stick I2 and its associated operating components. In operation,

the picker stick 12 moves within an operating cycle that includes three basic positions. With reference par- 4 ticularly to FIG. 1, the picker Stick 12 is in the position labelled] at which point the picker stick has released the shuttle and thrown the shuttle across the loom to a second picker stick located on the opposite side of the loom. When thrown by the picker stick, the shuttle will be moving to the right as viewed in FIG. 1 and to the left as viewed in FIG. 2. After the picker stick 12 has thrown the shuttle, it is moved from the position 1 back to a position labelled 2 in FIG. 1 at which point the picker stick is ready to receive the shuttle as it is thrown back from the other side of the loom. Thus, as the shuttle is thrown from the opposite side of the loom, it will be moving in a direction to the left'of FIG. 1 and to the right of FIG. 2, and when the shuttle engages the picker stick 12 the momentum of the shuttle will cause the picker stick to move from position 2 to a position labelled 3 in FIG. 1. During movement of the picker stick from position 2 to position 3 there occurs a deceleration of the shuttle by the mechanism of the present invention whereby the shuttle is brought to a complete stop at position 3 of the picker stick 12. Subsequently, a conventional strap mechanism (not shown) will actuate the picker stick to move it rapidly from position 3 to position 1 whereby the shuttle is accelerated and thrown back across to the other side of the loom.

- It will be noted that the drawings merely illustrate the lower portion of the picker stick and the picker stick check mechanism. The portion of the picker stick which engages and throws the shuttle is located at the upper end of the picker stick and a detailed description thereof is not necessary for the purposes of the present invention. Accordingly, these portions of the picker stick and loom are not shown in the drawings since they may be configured in accordance with conventional practise and are structured in a manner well known in the prior art. It may be assumed for the purposes of the present description that the picker stick 12 shown in the drawings extends upwardly from the drawings and that there will be provided a lay beam and other shuttle directing elements which will be conventionally configured and which will enable the picker stick 12 to perform the functions of throwing and receiving the shuttle. Furthermore, the strap mechanism whereby the picker stick 12 is accelerated from position 3 to position 1 is also not shown inasmuch as this mechanism is fully conventional and already well known in the prior art. Therefore, it may be assumed that any suitable strap mechanism may be utilized in conjunction with the mechanism of the present invention in accordance with known principles.

The picker stick 12 is mounted upon a picker stick support member 14 by means of a clamp 16 which includes screw means 18 whereby the picker stick 12 may be removably secured upon the support member 14. The picker stick member 14 is pivotably secured at its upper end to a crank mechanism 20 which comprises a pivot shaft 22 upon which the member 14 is rotatably secured through a bearing assembly 24.-The lower end of the picker stick member 14 is rotatably attached by bearing means (not shown) to a pivot shaft 26 which is fixed upon a steady arm 28 by means of a set screw 30. The opposite end of the steady arm 28 is the steady arm bearings are provided at suitable locations.

The crank mechanism includes an adjustable clamping member 40 which is adjustably secured upon a main shaft 42 which is rotatively' driven by the clamping member 40 when the picker stick moves through its operating cycle. Motion of the picker stick leftwardly as viewed in FIG. 2 will cause clockwise rotation of the main shaft 42 by means of the crank mechanism 20, while rightward motion of the picker stick 12 will cause counterclockwise rotation of the main shaft 42. It will be apparent that this rotation of the main shaft 42 by the picker stick l2 is caused by virtue of the engagement of the picker stick support 14 upon the shaft 22 of the crank mechanism 20 which operates as a torque transmission member between the picker stick member 14 and the shaft 42.

Shock absorber means in the form of a rubber bumper 44 are mounted upon a flange 10b of the frame 10 by means of a screw device 46. The picker stick support member 14 includes an abutment surface 48 which is locatedto engage the bumper 44 when the picker stick 14 is at position 3 of its operating cycle. This occurs when the picker stick 12 moves to accelerate the shuttle to throw it across the loom. Engagement of the abutment surface 48 with the bumper 44 defines the limit of travel of the picker stick 12 on one side of its operating cycle as well as providing for absorption of the momentum which is developed when the picker stick is moving to accelerate the shuttle.

Referring now to FIG. 1 which shows the side of the device opposite to that shown inFIG. 2, it will be seen that the main shaft 42 extends from its connection with the clamping member 40 to the opposite side of the device shown in FIG. 1 where a cam 50 is fixedly mounted upon the shaft 42 to rotate therewith. The cam 50 is located within a box 52 a portion of which is formed integrally with the frame 10, with a removable cover 54 being provided for the box 52. A pair of cam follower members 56 and 58 extend to within the box 52 with each of the members 56, 58 having mounted, respectively, at one end thereof cam followers 60 and 62 which are positioned to engage in bearing relationship a bearing surface 64 formed peripherally about the cam 50. Each of the cam follower members 56 and 58is similarly structured as an elongated leverage arm and each comprises a central pivot shaft 66, with each of the pivot shafts 66 having their ends rotatably mounted, in a manner to be hereinafter more fully described, so that the cam follower members 56 and 58 will each rotate about the centers of their respective pivot shaft 66. .Each of the cam followers 60 and 62 is rotatably mounted upon the ends of its respective cam follower members 56 and 58 with the opposite ends of the members 56 and 58 being urged, respectively, by a pair of spring members 68 and-70 to pivot about the pivot shaft 66 in a manner whereby the followers 60 and 62 are spring biased against the bearing surface 54 of the cam 50.

Each of the springs 68 and 70 are held in compression between the respective ends of the members 56 and 58 and a pair of flanges 72 which extend integrally from the outside of the box 52. A pair of centrally located spring guide shafts 74 are mounted with one of their ends pivotally attached to a respective one of the cam follower members 56 and 58 by means of bearing assemblies 76, with the freeends of the guide shafts 74 extending into central apertures (not shown) formed internally within adjustment screws 78 which are threaded to engage internal threads (not shown) formed within the flanges 72. A pair of bearing washers 80 are engaged between the ends of the springs 68 and and the adjustment screws 78, so that by rotation of the adjustment screws 78 the washers may be moved to adjustably compress the springs 68 and 70. It will be apparent that as the adjustment screws 78 are turned to increase the compression force of the springs 68 and 70, the followers 60 and 62 will be urged with greater force against the bearing surface 64 of the cam 50 by virtue of rotation of the cam follower members 56 and 58 about their respective shafts 66. Thus, it will be clear that the amount of pressure by which the followers 60 and 62 are urged against the cam 50 may be adjusted by manipulation of the adjustment screws 78.

Inasmuch as the cam 50 is fixed to rotate with the main shaft 42, and since the shaft 42 has fixed thereupon the crank mechanism 20, it will be clear that forces tending to resist rotation of the cam 50 will be applied through the crank mechanism 20 to resist movement of the picker stick member 14 and, consequently, of the picker stick member 12 itself. Thus, it will be apparent that the cam and follower assembly located within the box 52 operates, in a manner to be more fully described, as a check or braking mechanism for the picker stick 12.

, Referring now to FIGS. 3a 30, there is shown the individual positions of the cam 50 for each of the positions 1, 2 and 3 of the picker stick 12 previously described. FIG. 3a shows the position of the cam 50 when the picker stick is in position 1. At this point,the picker stick has thrown the shuttle across the loom and the abutment surface 48 is in contact with the bumper 44. When this occurs, the cam follower 60 which is urged against the bearing surface 64 operates, by virtue of the profile of the cam surface 64 to apply a force to the cam 50 which causes the cam 50 to rotate clockwise as shown by the arrow to the position shown in FIG. 312. It will be noted that the profile of the cam 50 is formed with a protuberance 82 against which the follower 60 rests when the device is in position 1. Because of the pressure exerted by the spring 68, and due to the profile of the cam 50, the follower 60 urges the cam 50 to rotate until the follower 60 moves from engagement against the protuberance 82 into engagement with a dwell section 84. This rotation of the cam 50, whereby the follower 60 moves from engagement with protuberance 82 to engagement with dwell 84, imparts sufficient momentum to the picker stick to enable the cam 50 to continue rotatingso that the follower 60 overrides a protuberance 86, thereby bringing the follower 60 into engagement within a dwell section 88 formed as part of the cam profile. With the follower 60 in engagement with dwell section 88, the picker stick will be in position 2 shown'in FIG. 3b.

During the period of time that the cam 50 is rotating from the position shown in FIG. 3a to the position I shown in FIG. 3b, the follower 62 exerts little or no effect upon rotation of the cam 50 due to the fact that the section 90 of the bearing surface 64 with which the follower 62 is in contact is formed as the surface of a right circular cylinder thereby avoiding application of any rotative force upon the cam 50 by the follower 62. Thus, it will be seen that rotation of the cam 50 between the position shown in FIG. 3a and the position shown in FIG. 3b is effected solely by operation of the follower 60 and the bearing effect which it exerts against the bearing surface 64 of the cam 50. Furthermore, as the cam 50 moves from the position shown in FIG. 3b to the position shown in FIG. 3c, rotational forces are exerted thereupon only by the follower 62, with the follower 60 then traversing a portion of the bearing surface 64 which is formed as a right circular cylinder thereby avoiding any rotational effect upon the cam50 by the follower 60, as described hereinafter.

Movement of the picker stick 12 from position 2 to position 3 is caused by the impact of the shuttle against the upper end of the picker stick. It is during this portion of the picker stick operating cycle that the picker stick operates to decelerate the moving shuttle. Thus, the function of the cam 50 and the follower 62 during movement of the cam 50 from the position shown in FIG. 3b to the position shown in FIG. 3c is to apply a braking or decelerating force to the picker stick whereby the picker stick and the shuttle may be brought to a stopin a smooth a controlled manner. Again, this is effected by virtue of the particular profile which is formed on the cam 50 operating in conjunction with the biasing force which is applied to the follower 62 by the spring member 70. g

It will be noted that with the cam 50 in the position shown in FIG. 3b, the cam follower 62 will be in abutment with a dwell section 100. As the cam 50 is rotated clockwise to the position shown in FIG. 30 it becomes necessary for the follower 62 tooverride a protuberance 102. As a result, the follower 62 applies a force tending to resist rotation of the cam 50, which force operates to smoothly decelerate and bring to a stop the picker stick 12 and the shuttle which has been thrown into engagement therewith. It will be noted that as the follower 62 moves from engagement with dwell section 100 over the protuberance 102, the follower 60 is travellingacross a section 104 of the cam bearing surface 64 which is formed in the shape of a right circular cylinder and as a result the follower 60 exerts no effect upon the rotative action of the cam 50 during this portion of the picker stick operating cycle.

Once the picker stick has reached position 3 shown in FIG. 30, the strap mechanism (not shown) comes into operation and actuates the picker stick to move from position 3 to position lthereby hurling the shuttle back across the loom. During this portion of the operating cycle of the picker stick, the force exerted thereupon by the strap mechanism is sufficiently great to easily overcome any resistance which may be created by virtue of the engagement of the followers 60 and 62 with the bearing surface 64. Thus, as the picker stick is accelerated from position 3 to position 1, the cam 50 moves counterclockwise from the position shown in FIG. 3c to the position shown in FIG. 3a, whereupon the cycle previously described is repeated once again.

From'the foregoing description, it will be seen that the followers 60 and 62 are individually effective to control the operation of the picker stick over different portions of the picker stick cycle. The follower 60 operates to return the picker stick from position l to position 2 immediately after the shuttle has been thrown. The mechanism whereby this is accomplished is much simpler than has been heretofore known inthe prior art and involves merely the cooperation which occurs between the follower 60 and the engaging profile of the cam 50. Furthermore, it will be seen that with the followers 60 and 62 engaged, respectively, within the dwell sections 88 and 100, the picker stick may be brought from position 1 to position 2 in a very smooth and positive manner and will be firmly held there by the engagement of the followers 60 and 62within their respective dwell sections 88 and 100. As a result of this mode of operation, vibration or rocking of the picker stick is avoided and the picker stick is brought to rest at position 2 in a positive and smoothly controlled manner. Furthermore, the invention eliminates the need for friction type braking means and other devices previously used which not only failed to eliminate picker stick chatter, but which also was susceptible to excessive wear thereby requiring more frequent and costly replacement of parts. Additionally, it will be found that the check mechanism of the present invention involves a simpler structure than the structures previously used and is, therefor, easier and less costly to manufacture and assemble. Additionally, the braking action which occurs by engagement of the followers 62 upon the protuberance 102 to bring the picker stick to a halt at position 3 is effected more smoothly and with less wear and deterioration of parts. In addition to the compactness and simplicity-of design of the invention, there is enabled simple and easy adjustment of the operating characteristics of the check mechanism due to the arrangement whereby the pressure by which the followers 60 and 62 are brought into abutment with the cam 50 may be adjusted merely by manipulation of the adjustment screws 78. Consequently, uncontrollable fluctuations in the operation of the shuttle and the picker stick during different portions of the operating cycle of the picker stick may be compensated for by selective adjustment of the adjustment screws 78 to apply a desired pressure for either of the cams 60 and 62 depending upon operational requirements. For example, if a greater pressure is necessary to bring the picker stick from position 1 to position 2, this can be accomplished nearly by tightening the compression on the spring 68 in order to increase the pressure by which the follower 60 is urged against the cam 50. Similarly, in a situation where higher shuttle velocities require greater braking action, this can be easily accomplished merely by increasing the compression in the spring 70 thereby causing the follower 62 to bear against the cam 50 with greater pressure. Of course, the profile of the cam 50 is an additional consideration which can be adjusted or changed, for example by replacement of the cam 50 with a cam having a different profile, thereby further expanding the adjustability and versatility of the mechanism of the present invention. Furthermore, it will be apparent that the operational characteristics of the present invention may be easily and simply varied and adjusted by other means within the knowledge of those skilled in the art merely by adjusting or replacing various parts of the mechanism.

A second aspect of the invention depicted in FIGS. 4a c provides means whereby the relative angular positioning between the picker stick member 14 and the cam 50 may be selectively adjusted. The pivot shaft 22 which is fixedly connected to the adjustable clamping member 40, has the picker stick member 14 rotatively mounted thereon. The adjustable clamping member 40 is releasably fixed upon the main shaft 42, and the selective angular adjustment between the picker stick member 14 and the cam 50 is accomplished by altering the angular relationship between the adjustable clamping member 40 and the main shaft 42, in accordance with the mechanism of the present invention. As seen in FIGS. 4a c, the member 40 generally comprises a C-shaped configuration with an adjustment gap 104 being provided therein. The main shaft 42 is positioned within the C-shaped configuration of the member 40 and the member 40 is clamped about the main shaft 42 by tightening a pair of clamping screws 106, only one of which is visible in the diagrams of FIGS. 4a c. The clamping screws 106 are fitted into an L-shaped recess 108 which is cut into the exterior of the member 40 and the heads of the screws 106 abut a horizontal leg 110 of the L-shaped recess 108. The screws 106 comprise threaded shanks 112 which extend through the adjustment gap 104 and engage on the opposite side thereof threaded recesses 114. It will be apparent that tightening of the screws 106 will tend to close the adjustment gap 104 thereby clamping the adjustable clamping member 40 tightly about the main shaft 42. Conversely, loosening of the screws 106 will widen the gap 104 thereby permitting relative rotation between the main shaft 42 and the clamping member 40.

With the screws 106 in the loosened condition, adjustment of the angular relative positioning between the cam 50 and the picker stick member 14 is effected by rotation of an adjustment screw 116 which is threadly engaged within a threaded bore 118 extending into the clamping member 40. The main shaft 42 is formed with an L-shaped recess 120 which includes a horizontal leg 122 against which the bottom of the adjustment screw 116 abuts. Tightening of the adjustment screw 116 will cause the clamping member 40 torotate clockwise relative to the main shaft 42, and loosening of the screw 116 will effect opposite rotation thereof by means of the abutment between the bottom of the screw 116 and the horizontal leg 122. Thus, the screw 116 may be selectively adjusted to adjust the angular relative positioning between the clamping member 40 and the main shaft42 thereby effecting adjustment of the angular relative positioning between the picker stick member l'4-and the cam 50. The adjustment is effected by first loosening the screws 106, subsequently locating the screw 116 at the proper depth within the threaded bore 118 and then tightening the screws 106 to securely clamp the member 40 about the shaft 42. FIGS. 40, 4b and 4c illustrate three different relative angular positions which may be effected by adjustment of the screw 116. In FIG. 4b the clamping member 40 has been rotated clockwise relative to the shaft 42 from the position shown in FIG. 4a. By loosening the screw 116, the clamping member 40 may be rotated counterclockwise relative to the shaft 42 from the position shown in 4a and this counterclockwise positioning is illustrated in FIG. 40.

By a third aspect of the present invention, there is provided a system for lubricating the various operating components of the mechanism depicted and described. The following description of this lubrication system will refer particularly to FIGS. 5, 6 and 7 of the drawings wherein various details of the system are shown. However, in order to fully comprehend the system of lubrication which is involved, it will be necessary to provide some additional details of the structure of the various operating components of the device.

FIGS. 5 and 6 depict in greater detail the cover 54. This member is removably mounted upon the box 52 by means of screws 124 which extend through openings 126 to engage threaded recesses 128 formed in the box 52. A pair of mounting posts 130 extend through openings 132 in the cover 54 in order to assure proper alignment of the cover 54 when it is mounted upon the box 52.

The inner side of the cover 54 is shown in FIG. 5. Located within the cover 54 are bearing means for rotatively supporting the central pivot shafts 66 of the cam follower members 56 and 58 and the main shaft 42. One end of each of the shafts 66 is rotatively mounted within a pair of pin bearings 136 located within the box 52, with only one of said bearings 136 being shown in FIG. 7. A central bearing assembly 138 mounted within a circular recess 140 in the cover 54 rotatively supports one end of the main shaft 42, with the opposite end being supported in another central bearing assembly (not shown) mounted within the box 52.

Each of the cam followers 60 and 62 is rotatively mounted upon an end of their respective cam follower members 56 and 58. In FIG. 7 there is shown an exemplary mounting for the cam follower 60, with the mounting for the cam follower 62 being identical therewith. The cam follower 60 comprises an annular ring supported upon a follower shaft 142-by means of a pin bearing comprising bearing-pins 144.

Lubricant for the bearings of the present invention is introduced through a lubricant inlet 146 formed in the side of the cover 54 which includes a lubricant fixture 148. The lubricant which is introduced flows through the inlet 146 into an annular channel 150 which extends about the circular recess 140 within which there is mounted the central bearing assembly 138 Thus, lubricant may be supplied to the central bearing 138 as well as to other parts of the assembly. From the annular channel 150, lubricant flows to a pair of auxiliary channels v1152 through which lubricant is supplied to the bearings 134 for the pivot shafts 66. Each of the bearings 134 is surrounded by an annular collar 154 which has a lubricant opening 156 located on one side thereof. Thus, the lubricant which flows through the auxiliary channels 152 is diverted around the'interior of the collar 154 through the space occupied by the pins of the bearing 134 and then throughan axial channel 158 formed centrally of the shaft 66. As shown by the arrows in FIGS. 5 and 6, lubricant flowing in the channel 158 will extend to the bearing 136 located in the opposite wall of the box 52 and also through vertical channels 160 which feed the bearing pins 144 for the cam follower 60. The follower 142 is provided with an axial channel 162 from which there is branched a feed channel l64, which supplies lubricant directly to the pins 144. It will be apparent that both of the bearings 134 as well as each bearing 136 is provided with lubricant by means similar to those described. Furthermore, it will be clear that the cam follower 62 willl be supplied with lubricant through the cam follower member 58 in a manner similar to that described in connection with the cam follower 60 and the cam follower member 56.

By virtue of the structure and arrangement of the present invention, several significant advantages may be achieved which are not obtainable with prior art devices. For example, with the adjustable means depicted.

and descirbed in connection with FIG. 4a c the ability l l to adjust the relative angular positioning of the picker stick and the cam 50 will enable the device of the present invention to be mounted with greater versatility upon a wider number of looms. Since different looms involve different structures insofar as the upper end of the picker stick and the shuttle are concerned, it becomes necessary to adjust the specific relative positioning of the various portions of the surface of the cam 50, depicted in FlGS. 3a c, so that the relative engagement between the followers 60 and 62 and the bearing surface 64 coincides with particular locations in the picker stick operating cycle. This adjustment is easily enabled by the method previously described whereby the clamping member 40 may be rotated relative to the main shaft 42.

Furthermore, it will be seen that the present invention, due to its simplicity of design and construction, enables provision of a highly simplified and effective lubrication system whereby all of the main operating components of the device will receive lubricant through a totally enclosed system having a single lubricant inlet. v

Although the present invention has been described with reference to a particular preferred embodiment thereof, it is to be understood that many alterations and modifications of the specific structure described may be effected by those skilled in the art without departure from the scope and purview of the invention.

What is claimed is: l

l. A mechanism for controlling operation of a loom picker stick comprising, in combination: a picker stick member mounted for reciprocal pivotal motion through an operating cycle; a rotatably mounted cam interconnected with said picker stick member to be simultaneously movable jointly therewith during said reciprocal motion of said picker stick through said operating cycle, said cam comprising a bearing surface extending circumferentially thereabout; a pair of cam follower members mounted to engage said cam bearing surface at different points thereon; spring means biasing said cam follower members to apply a force urging said cam follower members against said bearing surface; said cam bearing surface being particularly configured -to effect a desired action by each of said cam follower members upon said picker stick member whereby engagement of said pair of cam follower members against said bearing surface under the force of said spring bias serves to apply a force affecting rotation of said cam, said force being determined by the particular configuration of the portion of said cam bearing surface in engagement with said cam, follower members, respectively, and operating to control deceleration and positioning'of said picker stick member.

2. A mechanism according to'claim 1 wherein said cam bearing surface is configured to produce a different action upon said picker stick member by operation of each of said cam follower members.

3. A mechanism according to claim 1 wherein each of said cam follower members bears against a different portion, respectively, of said cam bearing surface during said picker stick operating cycle, with each of said respective portions being particularly shaped to produce a particular operating effect by each of said individual cam follower members.

4. A mechanism according to claim 1 wherein said picker stick is mounted to control operation of the shuttle of a loom, said picker stick cycle comprising a shuttle accelerating stroke and a shuttle decelerating stroke, with one of said cam follower members operating to apply a braking force to said picker stick only during said decelerating stroke, and with the other of said cam follower members operating to move said picker stick from a first position at the end of said accelerating stroke to a second position at the beginning of said decelerating stroke.

5. A mechanism according to claim 4 wherein said cam bearing surface is configured to releasably hold said picker stick in said second position at the beginning of said decelerating stroke by the action of said cam follower members bearing against said cam bearing surface.

6. A mechanism according to claim 1 wherein each of said cam follower members applies a force affecting rotation of said cam during different portions of said picker stick operating cycle.

7. A mechanism according to claim 6 wherein both said cam follower members operate to apply their respective forces to said picker stick member through portions of said operating cycle involving motion of said picker stick in the same direction.

8. A mechanism according to claim 6 wherein the configuration of said cam bearing surface is such that each of said cam follower members is rendered-ineffective to apply force to said picker stick during the portion of said operating cycle when the other of said cam follower members is applying a force thereto.

9. A mechanism according to claim 1 wherein said cam follower members each comprise an elongated leverage arm having a first and a second end, means pivotally mounting said arm at a point intermediate said ends for rotation thereabout, a cam follower mounted upon said arm at said first end, said spring means applying a force to said arm at said second end urging said arm to rotate about said intermediate pivot point in a direction to drive said cam follower against said cam bearing surface.

10. A mechanism according to claim 9 wherein said spring means include means for adjusting the force applied thereby to said second end of said leverage arm whereby the force with which said cam follower is driven against said cam bearing surface may be selectively adjusted.

11. A mechanism according to claim 9 wherein said intermediate pivot point of each of the leverage arms of said cam follower members is positioned to effect pivotal rotation of said leverage arm about an axis parallel to the axis of rotation of said cam.

12. A mechanism according to claim 9 wherein said cam follower members are mounted with said cam followers abutting said cam on opposite sides thereof.

13. A mechanism according to claim 1 comprising a crank mechanism interconnecting said picker stick member and said cam to effect simultaneous joint rotational movement thereof.

14. A mechanism according to claim 1 including means for selectively adjusting the relative angular relationship which exists between said picker stick member and said cam during operation of said picker stick through said picker stick operating cycle.

15. A mechanism according to claim 14 wherein said adjusting means comprise a crank mechanism mounted to transmit rotational force between said picker stick and said 'cam, said crank mechanism including screw means releasably fixing said crank mechanism to rotate with said cam said screw means being adjustably operable to alter the fixed angular relationship between said crank mechanism and said cam.

16. A mechanism according to claim 1 comprising a box-like enclosure having said cam and cam follower members operatively mounted therein, a pair of pivot shafts for rotatively mounting said cam follower members upon said enclosure, first bearing means arranged on said enclosure for rotatively supporting said pivot shafts, a cam follower operatively mounted upon each of said cam follower members, second bearing means rotatively mounting said cam followers upon said cam follower members, a main shaft for rotatively mounting said cam within said box-like enclosure, third bearing means for rotatively supporting said main shaft, a lubrication fluid inlet passage defined within a wall of said enclosure for feeding lubricating fluid to said third bearing means, lubricating fluid branch passages defined within the walls of said enclosure and extending between said third bearing means and each of said first bearing means, lubricating fluid transmission passages located centrally of said cam follower pivot shafts having one end in flow communication with said branch passages, and extending to effect flow of lubricating fluid to said first bearing means, and lubricating fluid diverting passages extending interiorly of said cam follower members between said centrally located transmission passages and said second bearing means to effect flow of lubricating fluid thereto, whereby each of the bearing means for said cam and said cam follower members may receive lubricating fluid from said lubricating fluid inlet passage through a totally enclosed lubricating fluid flow system defined within said box-like enclosure. 

1. A mechanism for controlling operation of a loom picker stick comprising, in combination: a picker stick member mounted for reciprocal pivotal motion through an operating cycle; a rotatably mounted cam interconnected with said picker stick member to be simultaneously movable jointly therewith during said reciprocal motion of said picker stick through said operating cycle, said cam comprising a bearing surface extending circumferentially thereabout; a pair of cam follower members mounted to engage said cam bearing surface at different points thereon; spring means biasing said cam follower members to apply a force urging said cam follower members against said bearing surface; said cam bearing surface being particularly configured to effect a desired action by each of said cam follower members upon said picker stick member whereby engagement of said pair of cam follower members against said bearing surface under the force of said spring bias serves to apply a force affecting rotation of said cam, said force being determined by the particular configuration of the portion of said cam bearing surface in engagement with said cam, follower members, respectively, and operating to control deceleration and positioning of said picker stick member.
 2. A mechanism according to claim 1 wherein said cam bearing surface is configured to produce a different action upon said picker stick member by operation of each of said cam follower members.
 3. A mechanism according to claim 1 wherein each of said cam follower members bears against a different portion, respectively, of said cam bearing surface during said picker stick operating cycle, with each of said respective portions being particularly shaped to produce a particular operating effect by each of said individual cam follower members.
 4. A mechanism according to claim 1 wherein said picker stick is mounted to control operation of the shuttle of a loom, said picker stick cycle comprising a shuttle accelerating stroke and a shuttle decelerating stroke, with one of said cam follower members operating to apply a braking force to said picker stick only during said decelerating stroke, and with the other of said cam follower members operating to move said picker stick from a first position at the end of said accelerating stroke to a second position at the beginning of said decelerating stroke.
 5. A mechanism according to claim 4 wherein said cam bearing surface is configured to releasably hold said picker stick in said second position at the beginning of said decelerating stroke by the actioN of said cam follower members bearing against said cam bearing surface.
 6. A mechanism according to claim 1 wherein each of said cam follower members applies a force affecting rotation of said cam during different portions of said picker stick operating cycle.
 7. A mechanism according to claim 6 wherein both said cam follower members operate to apply their respective forces to said picker stick member through portions of said operating cycle involving motion of said picker stick in the same direction.
 8. A mechanism according to claim 6 wherein the configuration of said cam bearing surface is such that each of said cam follower members is rendered ineffective to apply force to said picker stick during the portion of said operating cycle when the other of said cam follower members is applying a force thereto.
 9. A mechanism according to claim 1 wherein said cam follower members each comprise an elongated leverage arm having a first and a second end, means pivotally mounting said arm at a point intermediate said ends for rotation thereabout, a cam follower mounted upon said arm at said first end, said spring means applying a force to said arm at said second end urging said arm to rotate about said intermediate pivot point in a direction to drive said cam follower against said cam bearing surface.
 10. A mechanism according to claim 9 wherein said spring means include means for adjusting the force applied thereby to said second end of said leverage arm whereby the force with which said cam follower is driven against said cam bearing surface may be selectively adjusted.
 11. A mechanism according to claim 9 wherein said intermediate pivot point of each of the leverage arms of said cam follower members is positioned to effect pivotal rotation of said leverage arm about an axis parallel to the axis of rotation of said cam.
 12. A mechanism according to claim 9 wherein said cam follower members are mounted with said cam followers abutting said cam on opposite sides thereof.
 13. A mechanism according to claim 1 comprising a crank mechanism interconnecting said picker stick member and said cam to effect simultaneous joint rotational movement thereof.
 14. A mechanism according to claim 1 including means for selectively adjusting the relative angular relationship which exists between said picker stick member and said cam during operation of said picker stick through said picker stick operating cycle.
 15. A mechanism according to claim 14 wherein said adjusting means comprise a crank mechanism mounted to transmit rotational force between said picker stick and said cam, said crank mechanism including screw means releasably fixing said crank mechanism to rotate with said cam said screw means being adjustably operable to alter the fixed angular relationship between said crank mechanism and said cam.
 16. A mechanism according to claim 1 comprising a box-like enclosure having said cam and cam follower members operatively mounted therein, a pair of pivot shafts for rotatively mounting said cam follower members upon said enclosure, first bearing means arranged on said enclosure for rotatively supporting said pivot shafts, a cam follower operatively mounted upon each of said cam follower members, second bearing means rotatively mounting said cam followers upon said cam follower members, a main shaft for rotatively mounting said cam within said box-like enclosure, third bearing means for rotatively supporting said main shaft, a lubrication fluid inlet passage defined within a wall of said enclosure for feeding lubricating fluid to said third bearing means, lubricating fluid branch passages defined within the walls of said enclosure and extending between said third bearing means and each of said first bearing means, lubricating fluid transmission passages located centrally of said cam follower pivot shafts having one end in flow communication with said branch passages, and extending to effect flow of lubricating fluid to said first bearing means, and lubricating fluId diverting passages extending interiorly of said cam follower members between said centrally located transmission passages and said second bearing means to effect flow of lubricating fluid thereto, whereby each of the bearing means for said cam and said cam follower members may receive lubricating fluid from said lubricating fluid inlet passage through a totally enclosed lubricating fluid flow system defined within said box-like enclosure. 